WO2020161978A1 - Dispositif de transmission de puissance - Google Patents

Dispositif de transmission de puissance Download PDF

Info

Publication number
WO2020161978A1
WO2020161978A1 PCT/JP2019/044221 JP2019044221W WO2020161978A1 WO 2020161978 A1 WO2020161978 A1 WO 2020161978A1 JP 2019044221 W JP2019044221 W JP 2019044221W WO 2020161978 A1 WO2020161978 A1 WO 2020161978A1
Authority
WO
WIPO (PCT)
Prior art keywords
planetary reduction
reduction gear
gear
differential
bearing
Prior art date
Application number
PCT/JP2019/044221
Other languages
English (en)
Japanese (ja)
Inventor
忍足　俊一
Original Assignee
ジヤトコ株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ジヤトコ株式会社 filed Critical ジヤトコ株式会社
Priority to CN201980091534.0A priority Critical patent/CN113412378A/zh
Priority to JP2020570373A priority patent/JP6973966B2/ja
Priority to US17/428,531 priority patent/US11555536B2/en
Priority to EP19914317.3A priority patent/EP3922881A4/fr
Publication of WO2020161978A1 publication Critical patent/WO2020161978A1/fr

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0806—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts
    • F16H37/0813—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts with only one input shaft
    • F16H37/082—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts with only one input shaft and additional planetary reduction gears
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H48/11—Differential gearings with gears having orbital motion with orbital spur gears having intermeshing planet gears
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • B60K2001/001—Arrangement or mounting of electrical propulsion units one motor mounted on a propulsion axle for rotating right and left wheels of this axle
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2400/00—Special features of vehicle units
    • B60Y2400/70—Gearings
    • B60Y2400/73—Planetary gearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2410/00—Constructional features of vehicle sub-units
    • B60Y2410/102—Shaft arrangements; Shaft supports, e.g. bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/46—Systems consisting of a plurality of gear trains each with orbital gears, i.e. systems having three or more central gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
    • F16H2048/085—Differential gearings with gears having orbital motion comprising bevel gears characterised by shafts or gear carriers for orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H2048/106—Differential gearings with gears having orbital motion with orbital spur gears characterised by two sun gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • F16H2057/0216—Intermediate shaft supports, e.g. by using a partition wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F16H48/40—Constructional details characterised by features of the rotating cases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/037—Gearboxes for accommodating differential gearings
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears

Definitions

  • the present invention relates to a power transmission device.
  • Patent Documents 1 to 3 disclose power transmission devices.
  • the power transmission device of Patent Document 1 has three rotation shafts that are involved in rotation transmission arranged side by side, and it is easy to increase the size in the vertical direction (gravitational direction) (hereinafter referred to as the triaxial type).
  • the rotor of the motor is a hollow shaft, and the drive shaft penetrates the inside of this hollow shaft. Therefore, it is possible to reduce the size in the vertical direction as compared with the 3-axis type, but since the large counter gear is arranged, the size is increased in the vertical direction (hereinafter referred to as the 2-axis type). ..
  • the power transmission device of Patent Document 3 uses a planetary reduction gear having a stepped pinion instead of a counter gear, and enables size reduction in the vertical direction as compared with a two-axis type (hereinafter referred to as a single-axis type. I'll call it).
  • the reduction ratio tends to be smaller than that of the 2-axis type and the 3-axis type. Therefore, in the single-shaft type power transmission device, it is required to increase the reduction gear ratio and enhance the stability of the support of the differential gear.
  • the present invention is A motor, A first planetary reduction gear connected downstream of the motor; A second planetary reduction gear connected downstream of the first planetary reduction gear; A differential gear connected downstream of the second planetary reduction gear, A drive shaft connected downstream of the differential gear, The drive shaft is arranged so as to pass through an inner circumference of a rotor of the motor, an inner circumference of a sun gear of the first planetary reduction gear, and an inner circumference of a sun gear of the second planetary reduction gear.
  • the differential gear has a differential case,
  • the power transmission device is configured such that a part of the differential case located between the first planetary reduction gear and the second planetary reduction gear is supported on the inner peripheral side of the case member via a bearing.
  • the element that rotates in the same way as the differential gear of the 2nd planetary reduction gear and the differential case are integrated with high rigidity. Therefore, the element integrated with the differential case of the second planetary reduction gear is supported by the case member, which is the fixed-side member, via the bearing provided on the first planetary reduction gear side of the second planetary reduction gear. By adopting, it is possible to increase the reduction ratio and improve the stability of the support of the differential gear.
  • FIG. 4 is an enlarged view of a power transmission device and its surroundings.
  • FIG. 7 is an enlarged view around a reduction mechanism of a power transmission device according to a modification.
  • FIG. 1 is a diagram illustrating a power transmission device 1 according to this embodiment.
  • FIG. 2 is an enlarged view around the reduction mechanism 3 (the first planetary reduction gear 4, the second planetary reduction gear 5) of the power transmission device 1.
  • the power transmission device 1 includes a motor 2, a reduction mechanism 3 (first planetary reduction gear 4, second planetary reduction gear 5) that reduces the output rotation of the motor 2 and inputs the reduced rotation to a differential device 6, and a drive shaft 8 ( 8A, 8B).
  • a reduction mechanism 3 first planetary reduction gear 4, second planetary reduction gear 5 that reduces the output rotation of the motor 2 and inputs the reduced rotation to a differential device 6, and a drive shaft 8 ( 8A, 8B).
  • the speed reduction mechanism 3 (first planetary reduction gear 4, second planetary reduction gear 5), the differential device 6, and the drive shaft 8 (8A, 8A, 8B) are provided.
  • the output rotation of the motor 2 is decelerated by the reduction mechanism 3 and input to the differential device 6, and then via the drive shaft 8 (8A, 8B), the left and right drive wheels of the vehicle on which the power transmission device 1 is mounted.
  • the drive shaft 8A is connected to the left wheel of the vehicle equipped with the power transmission device 1 so as to be able to rotate
  • the drive shaft 8B is connected to the right wheel to be able to rotate.
  • first planetary reduction gear 4 is connected downstream of the motor 2
  • second planetary reduction gear 5 is connected downstream of the first planetary reduction gear 4.
  • the differential device 6 is connected downstream of the second planetary reduction gear 5, and the drive shafts 8 (8A, 8B) are connected downstream of the differential device 6.
  • the motor 2 has a cylindrical motor shaft 20, a cylindrical rotor core 21 externally mounted on the motor shaft 20, and a stator core 25 surrounding the outer periphery of the rotor core 21 at predetermined intervals.
  • the motor shaft 20 is provided so as to be relatively rotatable with respect to the drive shaft 8B in a state where the motor shaft 20 is externally attached to the drive shaft 8B.
  • bearings B1 and B1 are externally inserted and fixed to the outer peripheries of the one end 20a side and the other end 20b side in the longitudinal direction.
  • One end 20a side of the motor shaft 20 is rotatably supported by the cylindrical motor support portion 121 of the intermediate case 12 via the bearing B1.
  • the other end 20b side of the motor shaft 20 is rotatably supported by a cylindrical motor support portion 111 of the cover 11 via a bearing B1.
  • the motor 2 has a motor housing 10 that surrounds the outer periphery of the rotor core 21 at predetermined intervals.
  • the intermediate case 12 is joined to one end 10a of the motor housing 10, and the cover 11 is joined to the other end 10b of the motor housing 10.
  • Sealing rings S, S are provided at one end 10a and the other end 10b of the motor housing 10.
  • One end 10a of the motor housing 10 is joined to the annular base 120 of the intermediate case 12 without a gap by a seal ring S provided on the one end 10a.
  • the other end 10b of the motor housing 10 is joined to the annular joint portion 110 of the cover 11 without a gap by a seal ring S provided on the other end 10b.
  • the base portion 120 and the motor support portion 121 are provided with their positions displaced in the rotation axis X direction.
  • the motor support portion 121 is inserted inside the motor housing 10.
  • the motor support portion 121 is arranged on the inner diameter side of the coil end 253a, which will be described later, and faces the one end portion 21a of the rotor core 21 with a gap in the rotation axis X direction (see FIG. 2). Then, as shown in FIG. 2, the connecting portion 123 connecting the base portion 120 and the motor supporting portion 121 is provided so as to avoid contact between the coil end 253a and a side plate portion 452 described later.
  • a bearing retainer 125 is fixed to the end surface 121a of the motor support 121 on the rotor core 21 side.
  • the bearing retainer 125 has a ring shape when viewed from the rotation axis X direction.
  • the inner diameter side of the bearing retainer 125 is in contact with the side surface of the outer race B1b of the bearing B1 supported by the motor support portion 121 from the rotation axis X direction.
  • the bearing retainer 125 prevents the bearing B1 from falling off the motor support 121.
  • the joint portion 110 and the motor support portion 111 are provided with their positions displaced in the direction of the rotation axis X.
  • the motor support portion 111 is inserted inside the motor housing 10.
  • the motor support portion 111 is arranged on the inner diameter side of a coil end 253b, which will be described later, and faces the other end portion 21b of the rotor core 21 with a gap in the rotation axis X direction.
  • the connecting portion 115 that connects the joint portion 110 and the side wall portion 113 of the cover 11 is provided so as to avoid contact between the coil end 253b and the support cylinder 112 described later.
  • the rotor core 21 is arranged between the motor support portion 111 on the cover 11 side and the motor support portion 121 on the intermediate case 12 side.
  • the rotor core 21 is formed by laminating a plurality of silicon steel plates, and each of the silicon steel plates is externally attached to the motor shaft 20 in a state in which the relative rotation with the motor shaft 20 is restricted.
  • the silicon steel plate When viewed from the direction of the rotation axis X of the motor shaft 20, the silicon steel plate has a ring shape.
  • N and S pole magnets (not shown) alternate in the circumferential direction around the rotation axis X. It is provided in.
  • the one end 21 a of the rotor core 21 in the direction of the rotation axis X is positioned by the large diameter portion 203 of the motor shaft 20.
  • the other end 21b of the rotor core 21 is positioned by a stopper 23 press-fitted into the motor shaft 20.
  • the stator core 25 is formed by laminating a plurality of electromagnetic steel plates, and each of the electromagnetic steel plates is a ring-shaped yoke portion 251 fixed to the inner periphery of the motor housing 10, and the rotor core from the inner periphery of the yoke portion 251.
  • the tooth portion 252 protruding toward the 21 side is provided.
  • the stator core 25 having a configuration in which the winding wire 253 is distributed and wound over a plurality of teeth portions 252 is adopted.
  • the stator core 25 has coil ends 253a and 253b protruding in the rotation axis X direction. The length in the rotation axis direction is longer than that of the rotor core 21.
  • stator core having a configuration in which windings are concentratedly wound may be adopted for each of the plurality of teeth portions 252 protruding toward the rotor core 21 side.
  • the bearing B1 is press-fitted to the outer periphery of the region on the one end 20a side of the large diameter portion 203.
  • one side surface of the inner race B1a of the bearing B1 in the rotation axis X direction is in contact with a step portion 204 provided on the outer periphery of the motor shaft 20.
  • a ring-shaped stopper 205 press-fitted to the outer periphery of the motor shaft 20 is in contact.
  • the bearing B1 is positioned by the stopper 205 at a position where the inner race B1a is brought into contact with the step portion 204.
  • the one end 20a of the motor shaft 20 is located closer to the differential device 6 side (left side in the figure) than the stopper 205.
  • the one end 20a in the direction of the rotation axis X faces the side surface 41a of the sun gear 41 of the first planetary reduction gear 4 at a distance.
  • the cylindrical wall 122 is located radially outside the motor shaft 20.
  • the cylindrical wall 122 projects from the motor support 121 toward the differential device 6 side, and the tip 122a of the cylindrical wall 122 faces the side surface 41a of the sun gear 41 of the first planetary reduction gear 4 with a gap.
  • the cylindrical wall 122 surrounds the outer periphery of the motor shaft 20 at a predetermined interval, and a lip seal RS is installed between the cylindrical wall 122 and the motor shaft 20.
  • the lip seal RS is provided to partition a space Sa (see FIG. 1) on the inner diameter side of the motor housing 10 and a space Sb (see FIG. 1) on the inner diameter side of the intermediate case 12.
  • the space Sb on the inner diameter side of the intermediate case 12 communicates with the space Sc in the case 13 that houses the differential gear 6 described later.
  • Lubricating oil for the differential device 6 is sealed in the space Sb.
  • the lip seal RS is provided to prevent the lubricating oil from flowing into the space Sa on the inner diameter side of the motor housing 10.
  • the motor housing 10, the cover 11, the intermediate case 12, the case 13, and the intermediate cover 14 described later form a main body case 9 of the power transmission device 1.
  • the space Sa on the side of the motor housing 10 is a motor chamber that houses the motor 2 with the intermediate case 12 as a boundary.
  • the spaces Sb and Sc on the side of the case 13 are gear chambers that house the reduction mechanism 3 (the first planetary reduction gear 4 and the second planetary reduction gear 5). Then, the gear chamber is divided into a space Sb for accommodating the first planetary reduction gear 4 and a space Sc for accommodating the second planetary reduction gear 5 and the differential case 60 by an intermediate cover 14 described later.
  • the region 202 on the one end 20a side of the motor shaft 20 is formed with an inner diameter larger than the region 201 in which the rotor core 21 is externally inserted.
  • the cylindrical coupling portion 411 of the sun gear 41 is inserted inside the region 202 on the side of the one end 20a. In this state, the region 202 on the one end 20a side of the motor shaft 20 and the connecting portion 411 of the sun gear 41 are spline-fitted so that they cannot rotate relative to each other.
  • the output rotation of the motor 2 is input to the sun gear 41 of the first planetary reduction gear 4 via the motor shaft 20, and the sun gear 41 is rotated about the rotation axis X by the rotational driving force of the motor 2.
  • the sun gear 41 has a connecting portion 411 extending from the side surface 41a on the inner diameter side in the rotation axis X direction.
  • the connecting portion 411 is formed integrally with the sun gear 41, and a through hole 410 is formed across the inner diameter side of the sun gear 41 and the inner diameter side of the connecting portion 411.
  • the sun gear 41 is rotatably supported on the outer periphery of the drive shaft 8B that penetrates the through hole 410.
  • the ring gear 42 fixed to the inner circumference of the base 120 of the intermediate case 12 is located on the outer diameter side of the sun gear 41 in the radial direction of the rotation axis X.
  • a pinion gear 43 rotatably supported by a pinion shaft 44 meshes with the outer circumference of the sun gear 41 and the inner circumference of the ring gear 42. ..
  • the pinion gear 43 is rotatably supported on the outer circumference of the pinion shaft 44 via a needle bearing NB.
  • the pinion shaft 44 penetrates the pinion gear 43 in the direction of the axis X1 along the rotation axis X.
  • One end and the other end of the pinion shaft 44 in the longitudinal direction are supported by the pair of side plate portions 451 and 452 of the carrier 45.
  • the side plate portions 451 and 452 are provided in parallel with each other with an interval in the rotation axis X direction.
  • a plurality of (for example, four) pinion gears 43 are provided at predetermined intervals in the circumferential direction around the rotation axis X between the side plate portions 451 and 452.
  • the side plate portion 451 located on the differential device 6 side is provided with a cylindrical connecting portion 453.
  • the connecting portion 453 of the side plate portion 451 is arranged concentrically with respect to the rotation axis X, and projects along the rotation axis X in a direction approaching the differential device 6 (leftward in the drawing).
  • a ring-shaped intermediate cover 14 is located on the differential device 6 side when viewed from the intermediate case 12.
  • the intermediate cover 14 is provided in a state where the annular base portion 141 on the outer diameter side is sandwiched between the intermediate case 12 and the case 13.
  • the intermediate cover 14 is located between the first planetary reduction gear 4 and the second planetary reduction gear 5 that are lined up in the rotation axis X direction.
  • the intermediate cover 14 has a wall portion 142 extending from the annular base portion 141 toward the inner diameter side.
  • the wall portion 142 is provided in a direction orthogonal to the rotation axis X.
  • the inner diameter side of the wall portion 142 is inserted from the radial direction of the rotation axis X between the first planetary reduction gear 4 and the second planetary reduction gear 5 arranged side by side in the rotation axis X direction.
  • An opening 140 that penetrates the wall 142 in the thickness direction (direction of the rotation axis X) is provided on the inner diameter side of the wall 142.
  • the outer periphery of the opening 140 is provided at a position intersecting with the axis line X1 passing through the center of the pinion shaft 44 of the first planetary reduction gear 4.
  • the connecting portion 453 provided on the inner diameter side of the side plate portion 451 on the first planetary reduction gear 4 side is provided with a central opening 140 of the intermediate cover 14 (wall portion 142) on the left side from the motor 2 side to the differential device 6 side. Penetrates into.
  • the tip 453 a of the connecting portion 453 is located inside the case 13 attached to the intermediate cover 14.
  • the tip 453a of the connecting portion 453 in the direction of the rotation axis X faces the side surface 51a of the sun gear 51 of the second planetary reduction gear 5 with a gap.
  • a cylindrical connecting portion 511 extending from the sun gear 51 is inserted and spline-fitted, and the connecting portion 453 on the first planetary reduction gear 4 side and the second planetary reduction gear 5 side are connected.
  • the connecting portion 511 is connected to the inner diameter side of the intermediate cover 14 so as not to rotate relative to each other.
  • the sun gear 51 has a connecting portion 511 extending from the inner diameter side surface 51a in the rotation axis X direction.
  • the connecting portion 511 is formed integrally with the sun gear 51, and a through hole 510 is formed so as to extend across the inner diameter side of the sun gear 51 and the inner diameter side of the connecting portion 511.
  • the sun gear 51 is rotatably supported on the outer periphery of the drive shaft 8B that penetrates the through hole 510.
  • a side surface 51b of the sun gear 51 on the differential device 6 side faces a cylindrical support portion 601 of a differential case 60 described later with a gap in the rotation axis X direction between the side surface 51b and the support portion 601.
  • the sun gear 51 meshes with the large-diameter gear portion 531 of the stepped pinion gear 53 on the extension of the connecting portion 542 on the side of the first planetary reduction gear 4 described above.
  • the stepped pinion gear 53 has a large-diameter gear portion 531 that meshes with the sun gear 51, and a small-diameter gear portion 532 that has a smaller diameter than the large-diameter gear portion 531.
  • the stepped pinion gear 53 is a gear component in which a large-diameter gear portion 531 and a small-diameter gear portion 532 are integrally provided with a large-diameter gear portion 531 and a small-diameter gear portion 532 aligned in the direction of the axis X2 parallel to the rotation axis X.
  • the stepped pinion gear 53 has a through hole 530 that penetrates the inner diameter sides of the large diameter gear portion 531 and the small diameter gear portion 532 in the direction of the axis X2.
  • the stepped pinion gear 53 is rotatably supported on the outer periphery of the pinion shaft 54 that penetrates the through hole 530 via a needle bearing NB.
  • One end and the other end in the longitudinal direction of the pinion shaft 54 are supported by a side plate portion 651 integrally formed with the differential case 60 and side plate portions 551 arranged at intervals in the side plate portion 651.
  • the side plate portions 651 and 551 are provided in parallel with each other with an interval in the rotation axis X direction.
  • a plurality of stepped pinion gears 53 (for example, three) are provided at predetermined intervals in the circumferential direction around the rotation axis X between the side plate portions 651 and 551.
  • Each of the small diameter gear parts 532 meshes with the inner circumference of the ring gear 52.
  • the ring gear 52 is spline-fitted to the inner circumference of the case 13, and the ring gear 52 is restricted from rotating relative to the case 13.
  • a cylindrical portion 552 that extends toward the first planetary reduction gear 4 side is provided on the inner diameter side of the side plate portion 551.
  • the tubular portion 552 penetrates the central opening 140 of the intermediate cover 14 (wall portion 142) from the differential device 6 side to the motor 2 side (right side in the drawing).
  • the tip end 552a of the tubular portion 552 faces the side plate portion 451 of the carrier 45 of the first planetary reduction gear 4 with a space in the direction of the rotation axis X.
  • the tubular portion 552 is located radially outside the meshing portion of the connecting portion 453 on the first planetary reduction gear 4 side and the connecting portion 511 on the second planetary reduction gear 5 side.
  • the bearing B2 fixed to the opening 140 of the intermediate cover 14 (wall 142) is in contact with the outer periphery of the tubular portion 552.
  • the tubular portion 552 of the side plate portion 551 is rotatably supported by the intermediate cover 14 via the bearing B2.
  • the carrier 55 (side plate portions 551 and 651, the pinion shaft 54) of the second planetary reduction gear 5 is formed substantially integrally with the differential case 60.
  • the output rotation of the motor 2 reduced in speed by the first planetary reduction gear 4 is input to the sun gear 51.
  • the output rotation input to the sun gear 51 is input to the stepped pinion gear 53 via the large-diameter gear portion 531 meshing with the sun gear 51, and the stepped pinion gear 53 rotates about the axis X2.
  • the small-diameter gear portion 532 integrally formed with the large-diameter gear portion 531 rotates around the axis X2 integrally with the large-diameter gear portion 531.
  • the small-diameter gear portion 532 meshes with the ring gear 52 fixed to the inner circumference of the case 13. Therefore, when the small diameter gear portion 532 rotates about the axis X2, the stepped pinion gear 53 rotates about the rotation axis X while rotating about the axis X2.
  • the differential case 60 is interlocked with the circumferential displacement of the stepped pinion gear 53 around the rotation axis X. It rotates around the rotation axis X.
  • the outer diameter R1 of the small diameter gear portion 532 is smaller than the outer diameter R2 of the large diameter gear portion 531 (see FIG. 2).
  • the sun gear 51 serves as an output rotation input portion of the motor
  • the carrier 55 that supports the stepped pinion gear 53 serves as an input rotation output portion.
  • the rotation input to the sun gear 51 of the second planetary reduction gear 5 is greatly reduced by the stepped pinion gear 53, and then output to the differential case 60 in which the side plate portion 651 of the carrier 55 is integrally formed.
  • the differential case 60 is formed in a hollow shape in which the shaft 61, the bevel gears 62A and 62B, and the side gears 63A and 63B are housed inside.
  • tubular support parts 601 and 602 are provided on both sides in the direction of the rotation axis X (left and right direction in the drawing).
  • the support portions 601 and 602 extend along the rotation axis X in the direction away from the shaft 61.
  • connection piece 56 that connects the side plate portion 651 of the carrier 55 and the side plate portion 551 is provided on the outer diameter side of the support portion 601.
  • One end of the connection piece 56 on the differential case 60 side is provided so as to straddle the side plate portion 651 and the outer periphery of the differential case 60, and the other end is connected to the side plate portion 551 from the direction of the rotation axis X.
  • connection piece 56 is provided at a position avoiding interference with the stepped pinion gear 53 described above.
  • the plurality of stepped pinion gears 53 (for example, three) are provided at predetermined intervals in the circumferential direction around the rotation axis X.
  • the connection piece 56 is provided between the stepped pinion gears 53 that are adjacent to each other in the circumferential direction around the rotation axis X.
  • the inner race B2a of the bearing B2 is press-fitted on the outer periphery of the support portion 602 of the differential case 60.
  • the outer race B2b of the bearing B2 is held by the ring-shaped support portion 131 of the case 13, and the support portion 602 of the differential case 60 is rotatably supported by the case 13 via the bearing B2.
  • the drive shaft 8A penetrating the opening 130 of the case 13 is inserted into the support portion 602 from the rotation axis X direction, and the drive shaft 8A is rotatably supported by the support portion 602.
  • a lip seal RS is fixed to the inner circumference of the opening 130, and a lip portion (not shown) of the lip seal RS elastically contacts the outer circumference of the drive shaft 8A to open the outer circumference of the drive shaft 8A.
  • the gap with the inner circumference of the portion 130 is sealed.
  • the drive shaft 8B penetrating the opening 114 of the cover 11 is inserted into the support portion 601 from the rotation axis direction.
  • the drive shaft 8B is provided across the inner diameter side of the motor shaft 20 of the motor 2, the sun gear 41 of the first planetary reduction gear 4, and the sun gear 41 of the second planetary reduction gear 5 in the rotation axis X direction.
  • the tip side of the shaft 8B is rotatably supported by the support portion 601.
  • a lip seal RS is fixed to the inner circumference of the opening 114 of the cover 11, and a lip portion (not shown) of the lip seal RS elastically contacts the outer circumference of the drive shaft 8B, so that the drive shaft 8B is covered.
  • the gap between the outer circumference and the inner circumference of the opening 114 is sealed.
  • side gears 63A and 63B are spline-fitted to the outer circumferences of the tip ends of the drive shafts 8A and 8B, so that the side gears 63A and 63B and the drive shaft 8 (8A, 8B) rotate around the rotation axis X. Is integrally rotatably connected to.
  • the differential case 60 is provided with shaft holes 60a and 60b penetrating in a direction orthogonal to the rotation axis X at positions symmetrical with respect to the rotation axis X.
  • the shaft holes 60a and 60b are located on the axis line Y orthogonal to the rotation axis X, and the one end 61a side and the other end 61b side of the shaft 61 are inserted.
  • the one end 61a side and the other end 61b side of the shaft 61 are fixed to the differential case 60 by a pin P, and the shaft 61 is prohibited from rotating around the axis Y.
  • the lower side of the differential case 60 is immersed in the lubricating oil in the case 13.
  • the lubricating oil in the case 13 is adjusted to a height at which the one end 61a or the other end 61b of the shaft 61 is located at least in the lubricating oil. Is stored.
  • the shaft 61 is located between the side gears 63A and 63B in the differential case 60, and is arranged along the axis Y.
  • Bevel gears 62A and 62B are externally inserted and rotatably supported on a shaft 61 in the differential case 60.
  • Two bevel gears 62A and 62B are provided at intervals in the longitudinal direction of the shaft 61 (the axial direction of the axis Y), and the bevel gears 62A and 62B are arranged with their teeth facing each other. ing.
  • the bevel gears 62A and 62B are provided such that the shaft centers of the bevel gears 62A and 62B coincide with the shaft center of the shaft 61.
  • side gears 63A and 63B are located on both sides of the bevel gears 62A and 62B in the axial direction of the rotation axis X.
  • the side gears 63A and 63B are provided with two teeth spaced from each other in the axial direction of the rotating shaft X, with the tooth portions facing each other.
  • the bevel gears 62A and 62B and the side gears 63A and 63B are arranged to be separated from each other. It is assembled with the teeth engaged.
  • the differential case 60 rotates about the rotation axis X by the rotation input through the reduction mechanism 3 (the first planetary reduction gear 4 and the second planetary reduction gear 5).
  • the differential case 60 only one support portion 602 of the support portions 601 and 602 provided on both sides in the rotation axis X direction is supported by the case 13 via the bearing B2.
  • the second planetary reduction gear 5 (the small diameter gear portion 532 of the stepped pinion gear 53) is located on the outer diameter side of the other support portion 601. Therefore, the specifications are such that a member for supporting the differential case 60 cannot be provided on the outer diameter side of the support portion 602. Therefore, on the support portion 601 side of the differential case 60, the drive shaft 8B penetrating the support portion 601 is supported by the cover 11 via the bearing B1, so that the drive shaft 8B is indirectly supported by the cover 11. There is.
  • the carrier 55 of the second planetary reduction gear 5 located on the outer diameter side of the support portion 601 is formed integrally with the differential case 60. Therefore, the carrier 55 and the differential case 60 are integrally provided with predetermined rigidity and strength.
  • the intermediate cover 14 extending to the inner diameter side (rotation axis X side) is provided, and the pair of side plate portions 551 and 651 forming the carrier 55 are provided.
  • the bearing B3 fixed to the inner circumference of the opening 140 of the intermediate cover 14 (wall 142) is in contact with the outer circumference of the tubular portion 552, and the tubular portion 552 extending from the side plate portion 551 of the carrier 55 is Is rotatably supported by the intermediate cover 14 via the bearing B3.
  • the carrier 55 is formed substantially integrally with the differential case 60. Therefore, the tubular portion 552 of the carrier 55 can be regarded as a part of the differential case 60. Therefore, the tubular portion 552 that is a part of the differential case 60 is provided between the first planetary reduction gear 4 and the second planetary reduction gear 5 via the bearing B3 and the wall portion of the intermediate cover 14 that is the fixed side member. It is supported on the inner circumference of 142.
  • the tubular portion 552 of the carrier 55 integrally provided with the differential case 60 is the wall portion 142 of the intermediate cover 14 via the bearing B3. It is supported. This allows the differential case 60 to be indirectly supported by the intermediate cover 14 via the carrier 55 integrally formed with the differential case 60.
  • the support position by the intermediate cover 14 is closer to the differential case 60 than the support position by the cover 11. Therefore, by providing the intermediate cover 14 and indirectly supporting the differential case 60 with the intermediate cover 14, the support stability of the differential case 60 rotating around the rotation axis X is higher than that with the cover 11 only indirectly supporting. Is also raised.
  • the speed reduction mechanism 3 first planetary reduction gear 4, second planetary reduction gear 5
  • the differential device 6 the drive shaft 8 (8A, 8A, 8B) are provided.
  • the sun gear 41 is the output rotation input section of the motor 2
  • the carrier 45 that supports the pinion gear 43 is the input rotation output section.
  • the pinion gear 43 meshed with the outer circumference of the sun gear 41 and the inner circumference of the ring gear 42 rotates about the axis X1.
  • the ring gear 42 is spline-fitted to the inner circumference of the intermediate case 12 (fixed member), and its relative rotation with the intermediate case 12 is restricted. Therefore, the pinion gear 43 revolves around the rotation axis X while rotating around the axis X1.
  • the carrier 45 side plate portions 451 and 452 supporting the pinion gear 43 rotates about the rotation axis X at a rotation speed lower than the output rotation of the motor 2.
  • the connecting portion 453 of the carrier 45 is connected to the connecting portion 511 of the sun gear 51 on the second planetary reduction gear 5 side, and the rotation of the carrier 45 (the output rotation of the first planetary reduction gear 4) is 2 is input to the sun gear 51 of the planetary reduction gear 5.
  • the sun gear 51 is an output rotation input portion of the second planetary reduction gear 5
  • the carrier 55 that supports the stepped pinion gear 53 is an input rotation output portion. ing.
  • the stepped pinion gear 53 (the large diameter gear portion 531 and the small diameter gear portion 532) is rotated about the axis X2 by the rotation input from the sun gear 51 side.
  • the small diameter gear portion 532 of the stepped pinion gear 53 meshes with the ring gear 52 fixed to the inner circumference of the case 13. Therefore, the stepped pinion gear 53 rotates about the rotation axis X while rotating about the axis X2.
  • the carrier 55 (side plate portions 551, 651) supporting the stepped pinion gear 53 rotates about the rotation axis X at a lower rotation speed than the rotation input from the first planetary reduction gear 4 side.
  • the outer diameter R1 of the small diameter gear portion 532 is smaller than the outer diameter R2 of the large diameter gear portion 531 (see FIG. 2). Therefore, the rotation input to the sun gear 51 of the second planetary reduction gear 5 is reduced by the stepped pinion gear 53 to a greater extent than in the case of the first planetary reduction gear 4, and then the side plate portion 651 of the carrier 55 is integrated. Is output to the differential case 60 (differential device 6) formed on the.
  • the drive shaft 8 (8A, 8B) rotates around the rotation axis X by rotating the rotation of the differential case 60 about the rotation axis X by the input rotation, and the drive shaft 8 (8A, 8B) rotates to the left and right of the vehicle on which the power transmission device 1 is mounted. It is transmitted to drive wheels (not shown).
  • one of the support portions 601 and 602 provided on both sides in the rotation axis X direction is supported by the case 13 via a bearing B2.
  • the other support portion 601 is not supported by the fixed side member, but the tubular portion 552 of the carrier 55 that is integrally provided with the differential case 60 is supported by the intermediate cover 14 via the bearing B3.
  • 60 is indirectly supported by the intermediate cover 14 via the bearing B3.
  • the support positions of the bearings B2 and B3 are located on both sides of the position where the rotation of the differential case 60 is input from the second planetary reduction gear 5 (the engagement position between the side plate portion 651 and the pinion shaft 54). Therefore, the support stability of the differential case 60 that rotates around the rotation axis X by the input rotation is enhanced, and the stability of the differential device 6 (differential gear) is enhanced.
  • the first planetary reduction gear 4 and the second planetary reduction gear 5 that form the reduction mechanism 3 are arranged in series, and one of the second planetary reduction gears 5 is The pinion gear is a stepped pinion gear 53.
  • the reduction gear ratio in the reduction gear mechanism 3 can be made larger than in the case where the planetary reduction gears having a normal pinion gear (stepless pinion gear) are simply arranged in series. it can.
  • the intermediate cover 14 is provided between the first planetary reduction gear 4 and the second planetary reduction gear 5, and the tubular portion 552 of the carrier 55, which is integrally provided with the differential case 60, is intermediately provided via the bearing B3.
  • the cover 14 is supported.
  • one side (support portion 602) of the differential case 60 in the rotation axis X direction is supported by the case 13, and the other side (support portion 601 side) is indirectly supported by the intermediate cover 14.
  • the support stability of the differential case 60 that rotates around the rotation axis X is improved. Since the support stability of the differential case 60 is enhanced, the stability of the differential device 6 (differential gear) is also enhanced.
  • the power transmission device 1 has the following configuration.
  • the power transmission device 1 is Motor 2 and A first planetary reduction gear 4 connected downstream of the motor 2; A second planetary reduction gear 5 connected downstream of the first planetary reduction gear 4; A differential device 6 (differential gear) connected downstream of the second planetary reduction gear 5; A drive shaft 8 (8A, 8B) connected downstream of the differential gear.
  • the drive shaft 8B includes an inner diameter side of the rotor core 21 of the motor 2 (inner circumference of the rotor), an inner diameter side of the sun gear 41 of the first planetary reduction gear 4 (inner circumference), and an inner diameter of the sun gear 51 of the second planetary reduction gear 5. It is arranged so as to penetrate through the side (inner circumference).
  • the differential device 6 has a differential case 60 (differential case).
  • a tubular portion 552 which is a part of the differential case 60 and is located between the first planetary reduction gear 4 and the second planetary reduction gear 5 arranged in the rotation axis X direction, is provided with a bearing B3 (bearing). It is supported on the inner peripheral side of the intermediate cover 14 (case member).
  • the first planetary reduction gear 4 and the second planetary reduction gear 5 are arranged in series on the transmission path of the output rotation of the motor 2, and the planetary reduction gear has two stages, thereby reducing the reduction ratio. Can be increased.
  • the first planetary gear is used in the power transmission device 1 having the two-stage planetary reduction gears (the first planetary reduction gear 4 and the second planetary reduction gear 5). It is preferable to reduce the clearance between the reduction gear 4 and the second planetary reduction gear 5 in the rotation axis X direction. In such a case, the differential case 60 disposed downstream of the second planetary reduction gear 5 is in a floating state, and the stability of the differential case 60 is reduced.
  • a part of the differential case 60 is provided between the two planetary reduction gears (the first planetary reduction gear 4 and the second planetary reduction gear 5).
  • the cylindrical portion 552 located at is supported by the intermediate cover 14 via the bearing B3.
  • the power transmission device 1 has the following configuration.
  • (2) The differential rotation device 6 (differential gear) of the second planetary reduction gear 5 (the carrier 55: including the cylindrical portion 552) and the differential gear 6 and the differential case 60 (differential case) are integrated into a highly rigid structure. There is.
  • the elements (carrier 55, tubular portion 552) integrated with the differential case 60 in the second planetary reduction gear 5 are provided with a bearing B3 provided on the first planetary reduction gear 4 side, and an intermediate cover 14 which is a fixed member. Supported by.
  • the power transmission device 1 has the following configuration. (3) In the second planetary reduction gear 5, the sun gear 51 is an input element, the carrier 55 is an output element, and the ring gear 52 is a fixed element.
  • the differential case 60 is formed integrally with the carrier 55.
  • the tubular portion 552 of the carrier 55 is rotatably supported by the intermediate cover 14 via the bearing B3.
  • the rigidity of both the differential case 60 and the carrier 55 is increased, and as a result, the stability of the differential case 60 is increased. Further, since the differential case 60 and the carrier 55 are integrally formed, the fact that the differential case 60 is supported by the intermediate cover 14 (wall portion) means that the carrier 55 is supported by the intermediate cover 14 (wall portion). Since it is synonymous with this, the carrier 55 can also rotate stably.
  • the power transmission device 1 has the following configuration. (4)
  • the differential case 60 located on the opposite side of the second planetary reduction gear 5 is supported by the case 13 (case member) that houses the differential case 60 via the bearing B2 (bearing).
  • the differential case 60 is supported on both sides via the two bearings B2 and B3 (first bearing and second bearing), and the double-sided structure stabilizes the differential device 6. Sex increases.
  • the power transmission device 1 has the following configuration. (5) At the position on the inner peripheral side of the bearing B3 fixed to the inner periphery of the intermediate cover 14 (wall portion), the connecting portion 453 (output element) on the first planetary reduction gear 4 side and the second planetary reduction gear 5 The connection portion 511 (input element) on the side is engaged so as not to rotate relatively.
  • the power transmission device 1 can be downsized. In other words, in the radial direction of the rotation axis X (as viewed from the radial direction), the intermediate cover 14, the bearing B2 (bearing), the differential case 60, the connecting portion 453 (output element) of the first planetary reduction gear 4, The connecting portion 511 (input element) of the second planetary reduction gear 5 overlaps.
  • the power transmission device 1 has the following configuration. (6)
  • the main body case 9 (case member) has the wall portion 142 between the first planetary reduction gear 4 and the second planetary reduction gear.
  • the bearing B3 (bearing) is arranged on the inner circumference of the wall 142.
  • the tubular portion 552 that is a part of the differential case 60 is supported on the inner periphery of the wall portion 142 of the intermediate cover 14 via the bearing B3 (bearing).
  • the wall portion 142 is intentionally arranged between the first planetary reduction gear 4 and the second planetary reduction gear 5, and a part of the differential case 60 is provided.
  • a certain tubular portion 552 is supported on the inner circumference of the opening 140 of the wall portion 142 via a bearing B3.
  • the pinion gear 43 (pinion) of the first planetary reduction gear 4 is a stepless pinion gear
  • the pinion gear 53 of the second planetary reduction gear 5 is a stepped pinion.
  • the uniaxial type power transmission device 1 in order to increase the reduction ratio of the output rotation of the motor 2, it is conceivable to add a planet reduction gear (planetary gear mechanism) on the transmission route of the output rotation of the motor 2. ..
  • a planet reduction gear planetary gear mechanism
  • there are two types of pinion gears of the planetary reduction gears a stepped type that easily increases the reduction ratio and a stepless type that easily reduces the size. If only the size of the reduction gear ratio is pursued, the pinions of all planetary reduction gears may be stepped types, but in that case, the power transmission device 1 becomes large in the radial direction. That is, the problem of increasing the size remains.
  • the first planetary reduction gear 4 located downstream of the motor 2 and upstream of the second planetary reduction gear 5 is provided at a position sandwiched between the motor 2 and the second planetary reduction gear 5. Therefore, it is difficult to take a space around the first planetary reduction gear 4.
  • the second planetary reduction gear 5 located downstream of the second planetary reduction gear 5 and upstream of the differential device 6 is located between the first planetary reduction gear 4 and the differential case 60 of the differential device 6. Since it is provided, it is easier to take a space in the periphery than the first planetary reduction gear 4.
  • the reduction ratio can be increased while suppressing the size increase.
  • the differential case 60 and the stepped pinion gear 53 are made to overlap each other, and the bearings B2 and B3 are used to fix the differential case 60 to the fixed side member (case 13, intermediate cover 14). ), so that it is directly/indirectly supported.
  • FIG. 3A is an enlarged view around the reduction mechanism 3 of the power transmission device 1A according to the modification.
  • FIG. 3B is an enlarged view around the side plate portion 551A of the second planetary reduction gear 5.
  • the power transmission device 1A according to the modified example is different from the power transmission device 1 described above in that the power transmission device 1A does not include the intermediate cover 14.
  • the side plate portion 551A of the carrier 55 is supported on the inner circumference of the intermediate case 12 via a bearing B3.
  • the side plate portion 551AA is a ring-shaped plate member when viewed from the direction of the rotation axis X.
  • the side plate portion 551AA is provided in a direction orthogonal to the rotation axis X.
  • the inner diameter side of the side plate portion 551A extends to the rotation axis X side along the side plate portion 451 on the first planetary reduction gear 4 side.
  • the end portion 551a on the inner diameter side of the side plate portion 551A faces the outer periphery of the coupling portion 453 on the first planetary reduction gear 4 side with a radial gap.
  • the connecting portion 453 on the first planetary reduction gear 4 side and the connecting portion 511 on the second planetary reduction gear 5 side are spline-fitted on the inner diameter side of the side plate portion 551A. ..
  • the outer diameter side of the side plate portion 551A is the outer diameter side of the ring gear 42 of the first planetary reduction gear 4 and extends to the vicinity of the outer periphery 531a of the large diameter gear portion 531 of the second planetary reduction gear 5.
  • a cylindrical portion 553 extending toward the first planetary reduction gear 4 side is provided on the outer diameter side of the side plate portion 551A.
  • the tubular portion 553 is inserted from the rotation axis X direction into the recessed portion 124 provided in the base portion 120 on the outer diameter side of the intermediate case 12. In the recessed portion 124, the tubular portion 553 is provided so as to avoid contact with the base portion 120.
  • the recessed portion 124 of the base 120 is open to the second planetary reduction gear 5 side (left side in FIG. 3) on the outer diameter side of the region where the ring gear 42 of the first planetary reduction gear 4 is spline-fitted.
  • the recessed portion 124 is formed to have a depth Dx in the rotation axis X direction that extends to the outer diameter side of the ring gear 42.
  • the recessed portion 124 has a ring shape.
  • a step 127 for positioning the bearing B3 is provided on the outer diameter side of the recess 124.
  • the bearing B3 is inserted into the recess 124 from the second planetary reduction gear 5 side, and is positioned at a position where the outer race B3b is brought into contact with the step 127.
  • the bearing B3 is provided with a gap between it and the large diameter gear portion 531 on the second planetary reduction gear 5 side.
  • the inner race B3a of the bearing B3 is provided with a gap in the rotation axis X direction between the inner race B3a and the base portion 120, and the inner race B3a supports the outer periphery of the tubular portion 553 of the second planetary reduction gear 5. doing.
  • the tubular portion 553 of the side plate portion 551A of the second planetary reduction gear 5 is rotatably supported by the intermediate case 12 that is the fixed side member via the bearing B3.
  • the carrier 55 having the tubular portion 553 is formed substantially integrally with the differential case 60.
  • the tubular portion 553 can be regarded as a part of the differential case 60.
  • the tubular portion 553 that is a part of the differential case 60 is supported by the intermediate case 12 via the bearing B3 between the first planetary reduction gear 4 and the second planetary reduction gear 5 that are lined up in the rotation axis X direction. ..
  • the support portion 601 side of the differential case 60 in the rotation axis X direction is indirectly supported by the intermediate case 12. Therefore, the support stability of the differential case 60 when the differential case 60 rotates around the rotation axis X is enhanced.
  • the stability of the differential case 60 is increased, and thus the stability of the differential device 6 (differential gear) is also increased.
  • the power transmission device 1A according to the modification does not include the intermediate cover 14 of the power transmission device 1 described above. Therefore, the length L1 in the rotation axis X direction of the region where the connecting portion 453 on the first planetary reduction gear 4 side and the connecting portion 511 on the second planetary reduction gear 5 side are spline-fitted is the power transmission device 1.
  • the connecting portion 453 and the connecting portion 511 are shorter than the length L2 of the region where the spline fitting is performed.
  • tubular portion 553 on the second planetary reduction gear 5 side and the bearing B3 supporting the tubular portion 553 are located on the outer diameter side of the first planetary reduction gear 4.
  • the tubular portion 553 is provided in a positional relationship such that it overlaps with the first planetary reduction gear 4.
  • the first planetary reduction gear 4 and the second planetary reduction gear 5 are arranged closer to each other than in the case of the power transmission device 1 described above. Therefore, the size of the power transmission device 1A in the rotation axis X direction can be suppressed.
  • the power transmission device 1A has the following configuration.
  • the power transmission device 1A is Motor 2 and A first planetary reduction gear 4 connected downstream of the motor 2; A second planetary reduction gear 5 connected downstream of the first planetary reduction gear 4; A differential device 6 (differential gear) connected downstream of the second planetary reduction gear 5; A drive shaft 8 (8A, 8B) connected downstream of the differential gear.
  • the drive shaft 8B includes an inner diameter side of the rotor core 21 of the motor 2 (inner circumference of the rotor), an inner diameter side of the sun gear 41 of the first planetary reduction gear 4 (inner circumference), and an inner diameter of the sun gear 51 of the second planetary reduction gear 5. It is arranged so as to penetrate through the side (inner circumference).
  • the differential device 6 has a differential case 60 (differential case).
  • the tubular portion 553 of the carrier 55 which is a part of the differential case 60 and is located between the first planetary reduction gear 4 and the second planetary reduction gear 5 aligned in the rotation axis X direction, has a bearing B3 (bearing). It is supported via the inner peripheral side of the intermediate case 12 (case member).
  • the tubular portion 553 of the carrier 55 is supported by the intermediate case 12 via the bearing B3, so that the support portion 601 side of the differential case 60 in the rotation axis X direction is indirectly supported by the intermediate case 12. Supported. Thereby, the support stability of the differential case 60 when the differential case 60 rotates around the rotation axis X is enhanced. The stability of the differential case 60 is increased, and thus the stability of the differential device 6 (differential gear) is also increased.
  • the power transmission device 1A has the following configuration.
  • the tubular portion 553 of the carrier 55 is a part of the differential case 60 located between the first planetary reduction gear 4 and the second planetary reduction gear 5.
  • the tubular portion 553 of the carrier 55 is supported on the inner peripheral side of the intermediate case 12 (case member) via the bearing B3 (bearing).
  • the wall portion 142 disposed between the first planetary reduction gear 4 and the second planetary reduction gear 5 is not necessary, and is a part of the differential case 60.
  • the tubular portion 553 can be supported by the inner circumference of the intermediate case 12 that is the fixed-side member.
  • the intermediate cover 14 having the wall portion 142 can be omitted, the length of the power transmission device 1A in the rotation axis X direction can be made shorter than that of the power transmission device 1 described above by the amount of the intermediate cover 14 omitted.
  • the power transmission device 1A according to the modified example has the following configuration. (9)
  • the bearing B3 (bearing) overlaps the first planetary reduction gear 4 in the radial direction.
  • the first planetary reduction gear 4 When the power transmission device 1A is viewed from the radial direction of the rotation axis X, the first planetary reduction gear 4 is disposed so as to be hidden on the rotation axis side (inner diameter side) of the bearing B3. That is, since the bearing B3 and the first planetary reduction gear 4 are provided so as to have an overlapping range in the rotation axis X direction, the length of the power transmission device 1A in the rotation axis X direction is shortened by the overlapping range. it can.
  • the power transmission device 1A has the following configuration. (10) The bearing B3 (bearing) overlaps with the second planetary reduction gear 5 in the rotation axis X direction (axial direction).
  • the bearing B3 is provided so as to have a range overlapping with the first planetary reduction gear 4 in the rotation axis X direction, and the bearing B3 is provided in the radial direction of the rotation axis X with respect to the second planetary reduction gear 5. It is arranged closer to the inner diameter than the outer circumference.
  • the bearing B3 is arranged on the outer diameter side of the first planetary reduction gear 4 using a region lateral to the second planetary reduction gear 5 in the rotation axis X direction. The space in the power transmission device 1A can be utilized more effectively.
  • downstream connection in the present specification means that power is transmitted from a component arranged upstream to a component arranged downstream.
  • first planetary reduction gear 4 connected downstream of the motor 2
  • direct connection in the present specification means that members are connected to each other so that power can be transmitted without using another member such as a speed reducing mechanism, a speed increasing mechanism, or a speed change mechanism that changes a speed reduction ratio.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Retarders (AREA)
  • General Details Of Gearings (AREA)

Abstract

Le présent dispositif de transmission de puissance (1) comprend : un moteur (2) ; un premier engrenage de réduction planétaire (4) qui est relié au côté aval du moteur (2) ; un second engrenage de réduction planétaire (5) qui est relié au côté aval du premier engrenage de réduction planétaire (4) ; un dispositif différentiel (6) qui est relié au côté aval du second engrenage de réduction planétaire (5) ; des arbres d'entraînement (8A, 8B) qui sont reliés au côté aval d'un engrenage différentiel ; et un carter d'engrenage différentiel (60). L'arbre d'entraînement (8B) est disposé de manière à passer à travers le côté de diamètre interne d'un noyau de rotor (21), le côté de diamètre interne d'un pignon planétaire (41) du premier engrenage de réduction planétaire (4), et le côté de diamètre interne d'un pignon planétaire (51) du second engrenage de réduction planétaire (5). Une section cylindrique (552), qui est une partie du carter d'engrenage différentiel (60) et est positionnée entre le premier engrenage de réduction planétaire (4) et le second engrenage de réduction planétaire (5) qui sont alignés dans une direction X d'axe de rotation, est supportée sur le côté circonférentiel interne d'un couvercle intermédiaire (14) au moyen d'un palier (B3).
PCT/JP2019/044221 2019-02-08 2019-11-12 Dispositif de transmission de puissance WO2020161978A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
CN201980091534.0A CN113412378A (zh) 2019-02-08 2019-11-12 动力传递装置
JP2020570373A JP6973966B2 (ja) 2019-02-08 2019-11-12 動力伝達装置
US17/428,531 US11555536B2 (en) 2019-02-08 2019-11-12 Power transmission device
EP19914317.3A EP3922881A4 (fr) 2019-02-08 2019-11-12 Dispositif de transmission de puissance

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2019-022134 2019-02-08
JP2019022134 2019-02-08

Publications (1)

Publication Number Publication Date
WO2020161978A1 true WO2020161978A1 (fr) 2020-08-13

Family

ID=71948098

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2019/044221 WO2020161978A1 (fr) 2019-02-08 2019-11-12 Dispositif de transmission de puissance

Country Status (5)

Country Link
US (1) US11555536B2 (fr)
EP (1) EP3922881A4 (fr)
JP (1) JP6973966B2 (fr)
CN (1) CN113412378A (fr)
WO (1) WO2020161978A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20230035884A1 (en) * 2020-01-14 2023-02-02 The Gleason Works Double differential reducer ultra-high reduction transmission

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001330111A (ja) * 2000-05-23 2001-11-30 Aisin Seiki Co Ltd 電気自動車用動力伝達装置の潤滑装置
JP2005125920A (ja) * 2003-10-23 2005-05-19 Hitachi Ltd 車両用出力伝達装置及びそれを用いた車両駆動用電機システム
JP2013221566A (ja) 2012-04-17 2013-10-28 Exedy Corp 電気自動車の動力伝達装置
JP2016089860A (ja) 2014-10-30 2016-05-23 アイシン精機株式会社 減速機の潤滑構造
JP2018103676A (ja) 2016-12-22 2018-07-05 本田技研工業株式会社 動力装置
JP2019074207A (ja) * 2017-10-13 2019-05-16 アイシン・エィ・ダブリュ株式会社 車両用駆動装置

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05116549A (ja) * 1991-10-24 1993-05-14 Aisin Aw Co Ltd 電気自動車用駆動装置
JP3463366B2 (ja) * 1994-08-09 2003-11-05 アイシン・エィ・ダブリュ株式会社 電気自動車用駆動装置
US6401850B1 (en) * 2001-03-14 2002-06-11 New Venture Gear, Inc. Electric drive axle for hybrid vehicle
US7244210B2 (en) 2003-10-23 2007-07-17 Hitachi, Ltd. Power transmission apparatus for vehicle and vehicle-driving electric machinery system using the same
US8049384B2 (en) * 2009-06-19 2011-11-01 GM Global Technology Operations LLC Electronic drive unit
JP2011256969A (ja) 2010-06-10 2011-12-22 Toyota Motor Corp 駆動装置の潤滑装置
DE102010036884B4 (de) * 2010-08-06 2023-08-10 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Antriebssystem und Kraftfahrzeug mit einem derartigen Antriebssystem
DE102011007270A1 (de) * 2011-04-13 2012-10-18 Schaeffler Technologies AG & Co. KG Antriebsvorrichtung mit wenigstens einer elektrischen Maschine und mit einer mittels Druckmittel betätigten Kupplung
DE102012009346A1 (de) * 2012-05-09 2013-11-14 ZG-Zahnräder und Getriebe GmbH Planeten-Koppelgetriebe, insbesondere für elektrische Achsantriebssysteme für Kraftfahrzeuge
JP6089514B2 (ja) * 2012-09-10 2017-03-08 株式会社ジェイテクト 減速機及びこれを備えたモータ回転力伝達装置ならびに四輪駆動車
US9821654B2 (en) * 2015-06-29 2017-11-21 GM Global Technology Operations LLC Transverse dual planetary system
US9950607B2 (en) * 2015-11-12 2018-04-24 GM Global Technology Operations LLC Powertrain with multi-planetary, single motor drive unit
DE102016205263B3 (de) * 2016-03-31 2017-06-08 Schaeffler Technologies AG & Co. KG Antriebseinheit mit einer Rotorwelle eines elektromotorischen Antriebs und mit einem Getriebe
US10253857B2 (en) * 2017-01-31 2019-04-09 Dana Heavy Vehicle Systems Group, Llc Multi-speed electric transaxle unit with co-axial shafts
DE102017107803B3 (de) * 2017-04-11 2018-06-21 Schaeffler Technologies AG & Co. KG Antriebsvorrichtung für ein Kraftfahrzeug
JP6619765B2 (ja) * 2017-04-11 2019-12-11 株式会社三共 遊技機
JP6518722B2 (ja) * 2017-06-19 2019-05-22 本田技研工業株式会社 動力装置の支持構造
WO2019039599A1 (fr) * 2017-08-25 2019-02-28 アイシン・エィ・ダブリュ株式会社 Dispositif d'entraînement pour véhicule
CN111133225A (zh) * 2017-10-13 2020-05-08 爱信艾达株式会社 车辆用驱动装置
CN111133232B (zh) * 2017-10-13 2023-07-25 株式会社爱信 车用驱动装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001330111A (ja) * 2000-05-23 2001-11-30 Aisin Seiki Co Ltd 電気自動車用動力伝達装置の潤滑装置
JP2005125920A (ja) * 2003-10-23 2005-05-19 Hitachi Ltd 車両用出力伝達装置及びそれを用いた車両駆動用電機システム
JP2013221566A (ja) 2012-04-17 2013-10-28 Exedy Corp 電気自動車の動力伝達装置
JP2016089860A (ja) 2014-10-30 2016-05-23 アイシン精機株式会社 減速機の潤滑構造
JP2018103676A (ja) 2016-12-22 2018-07-05 本田技研工業株式会社 動力装置
JP2019074207A (ja) * 2017-10-13 2019-05-16 アイシン・エィ・ダブリュ株式会社 車両用駆動装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3922881A4

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20230035884A1 (en) * 2020-01-14 2023-02-02 The Gleason Works Double differential reducer ultra-high reduction transmission
US11821492B2 (en) * 2020-01-14 2023-11-21 The Gleason Works Double differential reducer ultra-high reduction transmission

Also Published As

Publication number Publication date
CN113412378A (zh) 2021-09-17
JPWO2020161978A1 (ja) 2021-10-21
JP6973966B2 (ja) 2021-12-01
US20220154809A1 (en) 2022-05-19
EP3922881A1 (fr) 2021-12-15
EP3922881A4 (fr) 2022-03-16
US11555536B2 (en) 2023-01-17

Similar Documents

Publication Publication Date Title
WO2010079683A1 (fr) Dispositif de transmission de puissance à engrenage
US11802614B2 (en) Vehicle drive device
US20160325613A1 (en) Drive device for hybrid vehicle
JP7383860B2 (ja) 動力伝達装置
WO2020161978A1 (fr) Dispositif de transmission de puissance
JP2016138565A (ja) 減速機構および減速機付き駆動装置
JP2021008248A (ja) インホイールモータ型の車両駆動装置
JP7487438B2 (ja) 動力伝達装置
WO2020161979A1 (fr) Dispositif de transmission de puissance
JP2020128789A (ja) 動力伝達装置
WO2020161977A1 (fr) Dispositif de transmission de puissance
JP2021107737A (ja) 動力伝達装置
JP2020128788A (ja) 動力伝達装置
WO2020183815A1 (fr) Dispositif de transmission de puissance
JP5385559B2 (ja) リング歯車を備える歯車伝動装置
JP2020143776A (ja) 動力伝達装置
JP7301465B2 (ja) 動力伝達装置
JP2020128790A (ja) 動力伝達装置
JP2020128792A (ja) 動力伝達装置
JP2020128793A (ja) 動力伝達装置
JP7210108B2 (ja) 動力伝達装置
JP2020159463A (ja) 動力伝達装置
JP2020044959A (ja) インホイールモータ型の車両駆動装置
JP2020204331A (ja) 動力伝達装置
JP2020128794A (ja) 動力伝達装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 19914317

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2020570373

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

ENP Entry into the national phase

Ref document number: 2019914317

Country of ref document: EP

Effective date: 20210908